EP2500530A1 - Engine waste heat recovery power-generating turbo system and reciprocating engine system provided therewith - Google Patents

Engine waste heat recovery power-generating turbo system and reciprocating engine system provided therewith Download PDF

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Publication number
EP2500530A1
EP2500530A1 EP10829792A EP10829792A EP2500530A1 EP 2500530 A1 EP2500530 A1 EP 2500530A1 EP 10829792 A EP10829792 A EP 10829792A EP 10829792 A EP10829792 A EP 10829792A EP 2500530 A1 EP2500530 A1 EP 2500530A1
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EP
European Patent Office
Prior art keywords
low
boiling
heat
engine
point medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP10829792A
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German (de)
English (en)
French (fr)
Inventor
Hirotaka Higashimori
Shinnosuke Osafune
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2500530A1 publication Critical patent/EP2500530A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/60—Application making use of surplus or waste energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/80—Size or power range of the machines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to an engine-waste-heat-recovery power generating turbo system and a reciprocating engine provided with the same.
  • a reciprocating engine takes in fuel, such as gasoline, alcohol, gas (natural gas, petroleum gas, etc.), and so forth, into a combustion chamber in a cylinder so as to have an appropriate mixing ratio with air, compresses it, and ignites it with an electrical spark to cause an explosion (rapid combustion).
  • the reciprocating engine causes a piston to reciprocate in the cylinder by using the force of this explosion, converts the reciprocation of the piston into continuous rotation by using a connecting rod and a crankshaft, and outputs motive force (shaft motive force) from the crankshaft.
  • the area surrounding the combustion chamber of the cylinder reaches a high temperature, it is cooled by cooling means.
  • a jacket-cooling-water circulation system is often employed, in which a double-structured space known as a jacket is formed around the cylinder, through which cooling liquid (for example, water, also referred to as jacket cooling water) is made to pass, and thus, overheating in the area surrounded by the cylinder is suppressed.
  • Reciprocating engines include reciprocating engines for traveling that are installed in traveling objects, such as automobiles, etc., and stationary reciprocating engines that are employed in a fixed state in power plants, etc.
  • the stationary reciprocating engine With regard to the stationary reciprocating engine, a system has been developed in which the shaft motive force is utilized at a maximum level, and, of the exhaust energy, pressure is recovered with a turbocharger and heat energy is recovered by means of, for example, heat utilization, such as producing hot water, etc.; and there have been efforts to improve the total efficiency of stationary reciprocating engines, including this recovered energy.
  • a stationary reciprocating engine a large, expensive cooling tower is provided in order to cool the jacket cooling water.
  • a so-called hybrid engine is a system invented to reduce this load fluctuation and to increase the average efficiency.
  • a hybrid engine is a system in which the load fluctuation in the engine is reduced and, at the time of low load, the motive force for generating power and driving is generated by using the shaft motive force, which increases the utilization efficiency of the shaft motive force.
  • the pressure of exhaust energy is also recovered with a turbocharger.
  • Patent Literature 1 With respect to vehicular reciprocating engines, as disclosed in, for example, Patent Literature 1, there is a known waste-heat recovery device that recovers waste heat generated in association with driving of an engine by utilizing the Rankine cycle.
  • This is a device in which the jacket-cooling-water circulation system is formed as a sealed structure; a turbine is driven with gasified cooling water, i.e., steam, heated with the waste heat from the engine; and the heat energy possessed by the steam is recovered by being converted to electrical energy, etc.
  • gasified cooling water i.e., steam
  • the jacket cooling water that is to say, water
  • the turbine needs to be rotated at a high speed.
  • a high-speed compatible turbine there is a problem in that, because of restrictions on practical rotational speed, the diameter of the turbine itself increases, resulting in an increased size.
  • a generator for the electrical energy conversion must have such a frequency so high that it cannot be provided for practical use with current technology.
  • a gear with a large reduction ratio is required for the turbine.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a practical engine-waste-heat-recovery power generating turbo system that recovers energy discarded from an engine as electrical power and a reciprocating engine provided with the same.
  • a first aspect of the present invention is an engine-waste-heat-recovery power generating turbo system that generates power by using waste heat from a reciprocating engine which has a jacket-cooling-water circulation system for cooling inside an engine jacket and an exhaust-gas channel for exhausting high-temperature combustion gas as exhaust gas
  • the engine-waste-heat-recovery power generating turbo system including a medium circuit that forms a closed-loop Rankine cycle, in which low-boiling-point medium whose critical temperature is from about 80 °C to about 200 °C is used, with an evaporator that converts the low-boiling-point medium to a gas phase, a turbine that expands the low-boiling-point medium, which has been converted to the gas phase at the evaporator, to convert the low-boiling-point medium to low-pressure gas phase, a condenser that cools the low-pressure
  • the low-boiling-point medium sequentially circulates through the compressor, the evaporator, the turbine, and the condenser.
  • the compressor pressurizes the low-boiling-point medium from a state in which it is in a low-pressure, low-temperature, liquid phase to a state in which it is in a high-pressure liquid phase.
  • the evaporator increases the temperature of the low-boiling-point medium, thus causing it to be in a state in which it is in a high-pressure, high-temperature gas phase.
  • the low-boiling-point medium in this state is introduced to the turbine to be expanded, thus being converted to a low-pressure gas phase.
  • the low-boiling-point medium converted to the low-pressure gas phase is cooled at the condenser, thus being converted to the low-pressure, low-temperature liquid phase.
  • the expanding low-boiling-point medium performs work, thereby rotating the turbine, and thus, the generator is driven to generate power.
  • the evaporator is provided with the first heat exchanger that performs heat exchange between the exhaust gas and the low-boiling-point medium to convert the low-boiling-point medium to the gas phase, the temperature of the low-boiling-point medium is increased by the exhaust gas that passes through the exhaust-gas channel.
  • the low-boiling-point medium that circulates in the medium circuit can recover heat from the exhaust gas discarded from the reciprocating engine (exhaust loss). Because the recovered energy is converted to electrical power, the waste heat from the reciprocating engine can be converted to highly versatile electricity.
  • the critical temperature of the low-boiling-point medium is from about 80 °C to about 200 °C, sufficient gas-phase pressure, temperature, etc. that are necessary to maintain a required turbine efficiency can be obtained even with comparatively low-temperature exhaust gas. Because the adiabatic heat drop for the low-boiling-point medium is reduced, the turbine can be rotated at low speed. Accordingly, it is possible to prevent an increase in the turbine size. Because the medium circuit is provided separately from the jacket-cooling-water circulation system and the exhaust channel, in other words, provided separately and independently of the reciprocating engine, it is possible to prevent the jacket-cooling-water circulation system, the exhaust channel, etc. from becoming complex. Accordingly, it is possible to provide a practical engine-waste-heat-recovery power generating turbo system that can be installed in, for example, a small space in a vehicle, etc., without greatly affecting the reciprocating engine.
  • the evaporator may be provided with, on an upstream side of the first heat exchanger, a second heat exchanger that performs heat exchange between the low-boiling-point medium and jacket cooling water on a high-temperature side of the jacket-cooling-water circulation system to heat the low-boiling-point medium.
  • the low-boiling-point medium undergoes heat exchange on the upstream side of the first heat exchanger with the jacket cooling water on the high-temperature side of the jacket-cooling-water circulation system by means of the second heat exchanger, thus increasing the temperature thereof; therefore, the jacket cooling water is cooled, and, on the other hand, the low-boiling-point medium can recover heat from the jacket cooling water. In this way, it is possible to eliminate the need to externally release the heat to cool the jacket cooling water (cooling loss) or to considerably reduce the amount thereof.
  • the low-boiling-point medium recovers the heat, which has conventionally been externally released, by means of the second heat exchanger, thereby making it possible to generate power with it, the efficiency of the reciprocating engine can be improved even more.
  • the jacket cooling water is generally from 80 to 85 °C
  • liquid-liquid heat exchange occurs with the low-boiling-point medium whose critical temperature is from about 80 °C to about 200 °C. Accordingly, a comparatively small liquid-liquid heat exchanger can be employed as the second heat exchanger.
  • the reciprocating engine may be provided with a turbocharger that compresses and supplies air; and the evaporator may be provided with, on the upstream side of the first heat exchanger, a third heat exchanger that performs heat exchange between the low-boiling-point medium and outlet air of the turbocharger to heat the low-boiling-point medium.
  • the outlet air from the turbocharger is compressed, the temperature thereof is increased. Because the density is decreased when the temperature is increased, there are systems in which the heat is externally released, and the outlet air is cooled and supplied to the cylinders to supply a greater amount of air to the cylinders.
  • the outlet air is cooled, and, on the other hand, the low-boiling-point medium can recover heat from the outlet air. Accordingly, because it is possible to eliminate the need to externally release the heat to cool the outlet air and because power can be generated, on the other hand, by recovering the heat energy thereof, the efficiency of the reciprocating engine can be improved.
  • the third heat exchanger may be provided in series on an upstream side or a downstream side of the second heat exchanger. Furthermore, with the above-described configuration, the third heat exchanger may be provided in parallel with the second heat exchanger.
  • the compressor be a turbo pump; that the turbo pump be coaxially connected to the generator; and that the turbine, the generator, and the turbo pump be accommodated in a sealed container.
  • the turbo pump is coaxially connected with the generator, the turbine, the generator, and the turbo pump are integrated. Because this integrated unit of the turbine, the generator, and the turbo pump is accommodated in the sealed container, it is not necessary to provide a seal between the turbine and the external air nor between the turbo pump and the external air. In addition, by sealing up these three components, including the generator, in a combined form, it is possible to reliably prevent the low-boiling-point medium from leaking.
  • a second aspect of the present invention is a reciprocating engine system including a reciprocating engine which has a jacket-cooling-water circulation system for cooling inside an engine jacket and an exhaust gas channel for exhausting high-temperature combustion gas as exhaust gas; and an engine-waste-heat-recovery power generating turbo system according to any one of Claims 1 to 6.
  • the evaporator is provided with the first heat exchanger that performs heat exchange at least between the exhaust gas and the low-boiling-point medium to convert the low-boiling-point medium to the gas phase, heat can be recovered from the exhaust gas discarded from the reciprocating engine. Because the recovered energy is converted to electrical power, the waste heat from the reciprocating engine can be converted to highly versatile electricity.
  • the critical temperature of the low-boiling-point medium is from about 80 °C to about 200 °C, it is possible to prevent an increase in size of the turbine, and it is possible to prevent the jacket-cooling-water circulation system, the exhaust-channel, etc. from becoming complex. Accordingly, it is possible to provide a practical engine-waste-heat-recovery power generating turbo system that can be installed in, for example, a small space in a vehicle, etc., without greatly affecting the reciprocating engine.
  • a reciprocating engine system 1 according to a first embodiment of the present invention will be described below with reference to Fig. 1 .
  • Fig. 1 is a block diagram showing, in outline, the configuration of the reciprocating engine system 1 according to the first embodiment.
  • the reciprocating engine system 1 is provided with a reciprocating engine 3 and an engine-waste-heat-recovery power generating turbo system 5.
  • the reciprocating engine 3 is provided with a plurality of cylinders 7 where fuel, such as gasoline, alcohol, gas (natural gas, petroleum gas, etc.), or the like, and air are taken in so as to be in an appropriate mixing ratio, compressed, and ignited, for example, with an electrical spark, to cause an explosion (rapid combustion); a jacket-cooling-water circulation system 9 that cools the area surrounding the combustion chambers of the cylinders 7; and a turbocharger 11 that increases the amount of air taken into the cylinders 7 by compressing the air taken thereinto.
  • fuel such as gasoline, alcohol, gas (natural gas, petroleum gas, etc.), or the like
  • air are taken in so as to be in an appropriate mixing ratio, compressed, and ignited, for example, with an electrical spark, to cause an explosion (rapid combustion)
  • a jacket-cooling-water circulation system 9 that cools the
  • the cylinders 7 are provided with an intake channel 13 through which the air is taken in and an exhaust channel (exhaust-gas channel) 15 through which combustion gas combusted in the cylinders 7 is expelled as exhaust gas.
  • the jacket-cooling-water circulation system 9 is provided with a jacket (engine jacket) 17 that forms double-structured spaces at the cylinders 7, in particular, around the combustion chambers thereof, a cooling water pump 19 that circulates the jacket cooling water, and a jacket-water circulation channel 21 that circulates the jacket cooling water by connecting the jacket 17, the cooling water pump 19, and the jacket 17.
  • the turbocharger 11 is mainly formed of a turbine 23 that is disposed in the exhaust channel 15 and that is rotationally driven by the exhaust gas from the cylinders 7 and a compressor 25 that is coaxially connected with the turbine 23 and that compresses the air passing through the intake channel 13 by being rotationally driven with the rotation of the turbine 23.
  • a cooling member that cools the air passing through the intake channel 13 may be provided in the intake channel 13, between the compressor 25 and the cylinders 7.
  • the engine-waste-heat-recovery power generating turbo system 5 is provided with a medium circuit 27 in which low-boiling-point medium circulates to form a closed-loop Rankine cycle, a generator 31, and a battery 33.
  • the low-boiling-point medium refers to, for example, a chlorofluorocarbon substitute, examples of which include HFC134a and HFE7100.
  • the low-boiling-point medium is not limited to these, and any medium may be employed so long as the critical temperature thereof is from about 80 °C to about 200 °C.
  • the critical temperature of HFC134a is 101.2 °C
  • the critical temperature of HFE7100 is 195.8 °C.
  • the medium circuit 27 is provided with an evaporator 33 that converts the low-boiling-point medium to a gas phase, a turbine 35 that expands the low-boiling-point medium that has been converted to the gas phase at the evaporator 33 to convert it to a low-pressure gas phase; a condenser 37 that cools the low-pressure-boiling-point medium from the turbine 35 to convert it to a liquid phase; a turbo pump (compressor) 39 that pressurizes the low-boiling-point medium sent from the condenser 37; and a medium channel 41 that connects these devices to circulate the low-boiling-point medium therein.
  • the evaporator 33 is provided with a jacket-cooling-water heat exchanger (second heat exchanger) 43 that performs heat exchange between the jacket cooling water on a high-temperature side of the jacket-water circulation channel 21 and the low-boiling-point medium, as well as an exhaust-gas heat exchanger (first heat exchanger) 45 that performs heat exchange between the exhaust gas that passes through the exhaust channel 15 and the low-boiling-point medium.
  • the jacket-cooling-water heat exchanger 43 is disposed on the upstream side of the exhaust-gas heat exchanger 45.
  • Jacket cooling water of, for example, 80 to 85 °C is supplied to the high-temperature side of the jacket-cooling-water heat exchanger 43, and, on the low-temperature side thereof, liquid-phase, high-pressure low-boiling-point medium of, for example, about 40 °C is supplied with a countercurrent system.
  • the jacket cooling water is cooled by the low-boiling-point medium by a few degrees, for example, 2 to 3 °C, at an outlet of the jacket-cooling-water heat exchanger 43.
  • the low-boing-point medium is heated by the jacket cooling water, and the temperature thereof is increased to, for example, about 75 °C at the outlet of the jacket-cooling-water heat exchanger 43.
  • the low-boiling-point medium can recover heat from the jacket cooling water. Because the critical temperature of the low-boiling-point medium is from about 80 °C to about 200 °C, liquid-liquid heat exchange occurs between the low-boiling-point medium and the jacket cooling water.
  • a liquid-liquid heat exchanger which can be made comparatively small, can be employed as the jacket-cooling-water heat exchanger 43. Furthermore, because the jacket-cooling-water heat exchanger 43 is a heat exchanger of a high-efficiency countercurrent system, the size thereof can be reduced further.
  • the liquid-phase, high-pressure low-boiling-point medium of, for example, about 75 °C is supplied with the countercurrent system (or a concurrent system).
  • the temperature of the low-boiling-point medium is increased by the exhaust gas that passes through the exhaust-gas channel, thus being converted to the gas phase.
  • the low-boiling-point medium can recover heat from the exhaust gas discarded from the cylinders 7.
  • the turbine 35 adiabatically expands the low-boiling-point medium that has been converted to the high-pressure, high-temperature gas phase at the evaporator 33, thus converting it to a low-pressure gas phase. At this time, the turbine 35 obtains work from expansion of the low-boiling-point medium and is rotated.
  • the turbine 35 is provided with a main shaft 47.
  • the generator 29 is integrated with the turbine 35 by being coaxially connected thereto via the main shaft 47.
  • the generator 29 is rotated by the rotation of the turbine 35 transmitted thereto via the main shaft 47 to generate power.
  • a synchronous generator or an induction generator is employed as the generator 29, and the main shaft 47 serves as the rotation shaft of a rotor in the generator 29.
  • the rotational speed of the generator 29 corresponds to the exhaust heat and temperature due to the engine load, and the flow volume and pressure can be changed by controlling the rotational speed.
  • the electric power from the power generation at the generator 29 charges the battery 31. Instead of charging the battery 31, the electric power may be directly supplied to devices that require it.
  • the condenser 37 is a heat exchanger that cools the low-pressure-boiling-point medium from the turbine 35, thereby converting it to the liquid phase.
  • the low-boiling-point medium of, for example, 80 °C is supplied, and, on the low-temperature side thereof, cooling air of, for example, about 20 °C is supplied as cooling medium with the concurrent system.
  • the low-boiling-point medium is cooled to, for example, about 40 °C by the cooling air.
  • the cooling air is heated by the low-boiling-point medium, and the temperature thereof is increased to, for example, about 50 °C at the outlet of the condenser 37.
  • gas such as air
  • liquid, such as water can be employed as the cooling medium.
  • the turbo pump 39 is coaxially connected with the turbine 35 and the generator 29 via the main shaft 47.
  • the turbo pump 39 is rotated by the rotation of the turbine 35 transmitted thereto via the main shaft 47 and pressurizes the liquid-phase low-boiling-point medium introduced thereto from the condenser 37 by compressing it.
  • the turbine 35, the generator 29, and the turbo pump 39 are integrated by being connected by the main shaft 47.
  • This integrated unit of the turbine 35, the generator 29, and the turbo pump 39 is accommodated in a container (sealed container) 49, which is sealed, so as to be isolated from the external air.
  • a container sealed container
  • the turbine 35, the generator 29, and the turbo pump 39 are accommodated in the container 49 and are isolated from the external air in this way, it is not necessary to provide seals between the turbine 35 and the external air as well as between the turbo pump 39 and the external air.
  • sealing up these three components, including the generator 29, in a combined form it is possible to reliably prevent the low-boiling-point medium from leaking. Therefore, the frequency of maintenance, such as exchanging sealing parts and replenishing working fluid, can be considerably reduced, and thus, the maintenance costs can be reduced.
  • the integrated unit of the turbine 35, the generator 29, and the turbo pump 39 is vertically disposed so that the main shaft 47 extends in a perpendicular direction and the turbo pump 39 is positioned at the bottom-most position. By doing so, the size of the equipment can be reduced, and the installation space can be made small. Furthermore, if imparted with a gas-liquid sealing function, a thrust bearing of the turbo pump 39 that supports the main shaft 47 can stably prevent the liquid-phase low-boiling-point medium from moving toward the generator 29 and the turbine 35.
  • the reciprocating engine system 1 configured as above, will now be described.
  • the exhaust gas from the cylinders 7 rotates the turbine 23.
  • the compressor 25 is rotationally driven to compress the air that is taken thereinto and to supply it to the cylinders 7 via the intake channel 13.
  • the temperature of the compressed air is increased to, for example, about 180 °C.
  • the air from the intake channel 13 and the separately supplied fuel are taken into the cylinders 7 through the motion of the pistons so as to achieve an appropriate mixing ratio.
  • the air and fuel that are taken thereinto are compressed and exploded (rapidly combusted).
  • the combusted combustion gas is expelled from the exhaust channel 15 as exhaust gas.
  • the reciprocating engine 1 causes reciprocating motion of the pistons in the cylinders with the force of this explosion, also converts this reciprocating motion of the pistons to continuous rotation with connecting rods and the crankshaft, and outputs the motive force (shaft motive force) from the crankshaft.
  • the jacket cooling water is made to circulate in the jacket-water circulation channel 21 by the cooling water pump 19.
  • the jacket cooling water obtains heat from the area surrounding the combustion chambers of the cylinders 7 and the temperature thereof is increased to, for example, 80 to 85 °C.
  • the heat in the area that surrounds the combustion chambers of the cylinders 7 is taken away, they are cooled.
  • the jacket cooling water undergoes heat exchange with the low-temperature, low-boiling-point medium flowing in the medium channel 41 by means of the jacket-cooling-water heat exchanger 43 to be cooled by, for example, a few degrees, and is then circulated to the jacket 17. Because the jacket cooling water is cooled by the low-boiling-point medium that circulates in the medium channel 41 in this way, it is possible to eliminate the need to externally release the heat to cool the jacket cooling water (cooling loss). Although the jacket cooling water is cooled at the jacket-cooling-water heat exchanger 43 only with the low-boiling-point medium in this embodiment, it is not limited thereto; for example, a conventional radiator may be provided in combination. By doing so, the degree of freedom in controlling the reciprocating engine 3 can be increased, in particular, at startup, at halting, and during partial-load operation.
  • the low-boiling-point medium that circulates in the medium channel 41 undergoes changes as follows.
  • the low-temperature (about 40 °C), low-pressure, liquid-phase low-boiling-point medium introduced from the condenser 37 is compressed at the turbo pump 39, which is rotated by the rotation of the turbine 35, thus being pressurized.
  • the pressurized low-temperature, high-pressure low-boiling-point medium is introduced to the jacket-cooling-water heat exchanger 43 in the evaporator 33 and is heated therein by the jacket cooling water, thus increasing the temperature thereof to, for example, about 75 °C at the outlet of the jacket-cooling-water heat exchanger 43.
  • the low-boiling-point medium is kept in the liquid phase.
  • the low-boiling-point medium is introduced to the exhaust-gas heat exchanger 45 in the evaporator 33, and the temperature thereof is increased by the exhaust gas of, for example, about 400 °C, which passes through the exhaust channel 15, thus being converted to the gas phase.
  • the exhaust gas for example, about 400 °C
  • the low-boiling-point medium that has been converted to the high-pressure, high-temperature gas phase at the evaporator 33 is introduced to the turbine 35 and is adiabatically expanded to be in the high-temperature, high-pressure gas phase or in a wet state in which a portion thereof is in the liquid phase.
  • the temperature of the low-boiling-point medium is, for example, about 80 °C.
  • the low-boiling-point medium can recover heat from the jacket cooling water at the jacket-cooling-water heat exchanger 43 and can recover heat from the exhaust gas discarded from the reciprocating engine 3 at the exhaust gas heat exchanger 45. Because the recovered heat (energy) is converted to electrical power by the generator 29, the waste heat from the reciprocating engine 3 can be converted to highly versatile electricity. Because of these, the efficiency of the reciprocating engine 3 can be improved considerably.
  • liquid-liquid heat exchange can be employed at the jacket-cooling-water heat exchanger 43, and, at the exhaust-gas heat exchanger 45, sufficient gas-phase pressure, temperature, etc. that are necessary to maintain a required turbine efficiency can be obtained even with comparatively low-temperature exhaust gas.
  • efficient heat exchange can individually be performed at the jacket-cooling-water heat exchanger 43 and the exhaust-gas heat exchanger 45. Because the adiabatic heat drop for the low-boiling-point medium is reduced, the turbine can be rotated at low speed. Accordingly, it is possible to prevent an increase in the turbine size.
  • the medium circuit 27 is provided separately from the jacket-cooling-water circulation system 9 and the exhaust channel 15, in other words, provided separately and independently of the reciprocating engine 3, it is possible to prevent the jacket-cooling-water circulation system 9, the exhaust channel 15, etc. from becoming complex. Accordingly, it is possible to provide a practical engine-waste-heat-recovery power generating turbo system 5 that can be installed in, for example, a small space in a vehicle, etc., without greatly affecting the reciprocating engine 3.
  • a reciprocating engine system 1 according to a second embodiment of the present invention will be described by using Fig. 2 .
  • the configurations of the evaporator 33 and the jacket-cooling-water circulation system 9 in the engine-waste-heat-recovery power generating turbo system 5 of this embodiment differ from those in the first embodiment, the different portions will mainly be described herein, and redundant descriptions will be omitted for the portions that are the same as those in the first embodiment. Note that the same members as those in the first embodiment are given the same reference signs.
  • Fig. 2 is a block diagram showing, in outline, the configuration of the reciprocating engine system 1 according to this embodiment.
  • the evaporator 33 of this embodiment is formed only with the exhaust-gas heat exchanger 45. Because of this, the jacket-cooling-water circulation system 9 is provided with a radiator 51 for cooling the jacket cooling water whose temperature is increased by the cylinders 7. A cooling tower may be employed instead of the radiator 51.
  • the jacket cooling water that is circulated by the cooling water pump 19 cools the area surrounding the combustion chambers of the cylinders 7 when passing through the jacket 17 and, at that time, the temperature thereof is increased by obtaining heat from the area that surrounds the combustion chambers of the cylinders 7.
  • the jacket cooling water is cooled at the radiator 51 through heat exchange with the cooling air and is then circulated to the jacket 17.
  • the low-temperature, high-pressure low-boiling-point medium sent from the turbo pump 39 is introduced to the exhaust-gas heat exchanger 45 in the evaporator 33.
  • the temperature of the low-boiling-point medium is increased by the exhaust gas of, for example, about 400 °C passing through the exhaust channel 15, thus being converted to a high-temperature, high-pressure gas phase.
  • the waste heat from the reciprocating engine 3 can be converted to highly versatile electricity.
  • the critical temperature of the low-boiling-point medium is from about 80 °C to about 200 °C, at the exhaust-gas heat exchanger 45, sufficient gas-phase pressure, temperature, etc. that are necessary to maintain a required turbine efficiency can be obtained even with comparatively low-temperature exhaust gas. Because the adiabatic heat drop for the low-boiling-point medium is reduced, the turbine can be rotated at low speed. Accordingly, it is possible to prevent an increase in the turbine size.
  • the medium circuit 27 is provided separately from the jacket-cooling-water circulation system 9 and the exhaust channel 15, in other words, provided separately and independently of the reciprocating engine 3, it is possible to prevent the jacket-cooling-water circulation system 9, the exhaust channel 15, etc. from becoming complex. Accordingly, it is possible to provide a practical engine-waste-heat-recovery power generating turbo system 5 that can be installed in, for example, a small space in a vehicle, etc., without greatly affecting the reciprocating engine 3.
  • the engine-waste-heat-recovery power generating turbo system 5 of this embodiment can be applied to systems in which a sufficient heat source can be ensured for the exhaust-gas heat exchanger 45 by means of a boiler, a gas turbine, etc.
  • a reciprocating engine system 1 according to a third embodiment of the present invention will be described by using Fig. 3 .
  • the configurations of the evaporator 33 and the intake channel 13 in the engine-waste-heat-recovery power generating turbo system 5 of this embodiment differ from those in the first embodiment, the different portions will mainly be described herein, and redundant descriptions will be omitted for the portions that are the same as those in the first embodiment. Note that the same members as those in the first embodiment are given the same reference signs.
  • Fig. 3 is a block diagram showing, in outline, the configuration of the reciprocating engine system 1 according to this embodiment.
  • an intake-air heat exchanger (third heat exchanger) 53 is provided between a blower 25 at the intake channel 13 and the cylinders 7.
  • a medium channel 41 is inserted at a position between the jacket-cooling-water heat exchanger 43 and the exhaust-heat heat exchanger 45 and is attached thereto.
  • the intake-air heat exchanger 53 is a heat exchanger that performs heat exchange between air (intake air) at the outlet of the turbocharger 11 (outlet of the compressor 25) and the low-boiling-point medium.
  • the evaporator 33 is formed of a heat exchanger in which the jacket-cooling-water heat exchanger 43, the intake-air heat exchanger 53, and the exhaust-gas heat exchanger 45 are connected in series in this order. Therefore, the intake-air heat exchanger 53 is provided on the upstream side of the exhaust-gas heat exchanger 45.
  • the intake-air heat exchanger 53 forms a portion of the intake channel 13, and air compressed by the blower, thus having a comparatively high temperature of, for example, about 180 °C, flows in the interior thereof.
  • the low-boiling-point medium of, for example, about 75 °C, that has flowed out from the jacket-cooling-water heat exchanger 43 is supplied to the medium channel 41, which is inserted inside the intake-air heat exchanger 53 and is attached thereto, with the countercurrent system relative to the intake air.
  • the intake air is cooled by the low-boiling-point medium, and, on the other hand, the low-boiling-point medium is heated by the intake air. In other words, the low-boiling-point medium can recover heat from the intake air.
  • the operation of the thus-configured reciprocating engine system 1 according to this embodiment is basically the same as that of the above-described first embodiment, redundant descriptions will be omitted, and only different portions will be described.
  • the intake air which is the outlet air from the turbocharger 11
  • the temperature thereof is increased.
  • this intake air is cooled by the low-boiling-point medium at the intake-air heat exchanger 53, the temperature thereof is decreased, thus making it possible to increase the density thereof. Accordingly, the amount of air supplied to the cylinders can be increased further.
  • the low-boiling-point medium that has exited the jacket-cooling-water heat exchanger 43 is introduced to the intake-air heat exchanger 53.
  • the temperature of the low-boiling-point medium is increased by the intake air that passes through the intake-air heat exchanger 53.
  • the low-boiling-point medium can recover the heat from the intake air, it is possible to eliminate the need to externally release the heat to cool the intake air. Therefore, at the evaporator 33, heat discarded from the reciprocating engine 3 can also be recovered at the intake-air heat exchanger 53 in addition to the jacket-cooling-water heat exchanger 43 and the exhaust-gas heat exchanger 45. Because the heat (energy) recovered in this way is converted to electrical power by the generator 29, the waste heat from the reciprocating engine 3 can be converted to highly versatile electricity.
  • the intake-air heat exchanger 53 in this embodiment is connected in series at the intermediate position between the jacket-cooling-water heat exchanger 43 and the exhaust-gas heat exchanger 45, it is not limited thereto.
  • the intake-air heat exchanger 53 may be disposed, for example, so as to be in parallel with the jacket-cooling-water heat exchanger 43.
  • the intake-air heat exchanger 53 may be employed in the engine-waste-heat-recovery power generating turbo system 5 of the second embodiment. In this case, the intake-air heat exchanger 53 is connected in series to the exhaust-gas heat exchanger 45 on the upstream side thereof.
  • a reciprocating engine system 1 according to a fourth embodiment of the present invention will be described by using Fig. 6 .
  • the configurations of the turbine 35 and the turbo pump 39 in the engine-waste-heat-recovery power generating turbo system 5 of this embodiment differ from those in the first embodiment, the different portions will mainly be described herein, and redundant descriptions will be omitted for the portions that are the same as those in the first embodiment. Note that the same members as those in the first embodiment are given the same reference signs.
  • Fig. 6 is a block diagram showing, in outline, the configuration of the reciprocating engine system 1 according to the fourth embodiment.
  • the turbine 33 and the generator 29 integrated with the main shaft 47 are accommodated in a container 55, which is sealed, so as to be isolated from the external air.
  • the turbo pump 39 is configured to be rotationally driven by the motor 57.
  • the motor 57 is driven by electrical power supplied from the battery 31.
  • the turbo pump 39 and the motor 57 are accommodated in a container 59, which is sealed, so as to be isolated from the external air.
  • the operation of the thus-configured reciprocating engine system 1 according to this embodiment is basically the same as that of the above-described first embodiment, redundant descriptions will be omitted, and only different portions will be described.
  • the low-boiling-point medium converted to the high-pressure, high-temperature gas phase at the evaporator 33 is introduced to the turbine 35 and is adiabatically expanded thereat to be in a high-temperature, low-pressure gas phase or in a wet state in which a portion thereof is in the liquid phase. Because the turbine 35 is rotated by obtaining work through the expansion of the low-boiling-point medium, the generator 29 is rotated via the main shaft 47, thus generating power. The electrical power generated at the generator 29 charges the battery 31.
  • the motor 57 is rotated by the electric power supplied from the battery 31, and thus, the turbo pump 39 is rotated.
  • the low-temperature, low-pressure liquid phase low-boiling-point medium introduced to the turbo pump 39 from the condenser 37 is pressurized by the turbo pump 39 by being compressed therein.
  • the turbine 35 and the generator 29 are accommodated in the container 55, the turbo pump 39 and the motor 57 are accommodated in the container 59, and thus, they are individually isolated from the external air; therefore, it is not necessary to provide a seal between the turbine 35 and the external air nor between the turbo pump 39 and the external air. Accordingly, because the low-boiling-point medium can be reliably prevented from leaking, the frequency of maintenance, such as exchanging seal parts and replenishing working fluid, can be considerably reduced, and thus, the maintenance costs can be reduced.
  • turbo pump 39 is not connected to the main shaft 47 of the turbine 35, the turbine 35 and the turbo pump 39 can have independent rotational speeds. Accordingly, the degree of freedom can be increased for controlling the engine-waste-heat-recovery power generating turbo system 5 and the reciprocating engine system 1.
  • the structures around the turbine 33 and the turbo pump 39 of this embodiment may be applied to the engine-waste-heat-recovery power generating turbo systems 5 of the second embodiment and the third embodiment described above.
  • turbo pump 39 is employed as a compressor, a known compressor of an appropriate type may be employed.
EP10829792A 2009-11-13 2010-09-30 Engine waste heat recovery power-generating turbo system and reciprocating engine system provided therewith Withdrawn EP2500530A1 (en)

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JP2009259888A JP2011106302A (ja) 2009-11-13 2009-11-13 エンジン廃熱回収発電ターボシステムおよびこれを備えた往復動エンジンシステム
PCT/JP2010/067074 WO2011058832A1 (ja) 2009-11-13 2010-09-30 エンジン廃熱回収発電ターボシステムおよびこれを備えた往復動エンジンシステム

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JP2011106302A (ja) 2011-06-02
KR20120058582A (ko) 2012-06-07
CN102549239A (zh) 2012-07-04

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